Hydrostatic brake system



Mam E@ 'w48 c. SAUZEDDE 1 253595363 HYDRosTATc BRAKE SYSTEM Filed IJec. l0, 1942 2 Sheets-Sheet l attorneys Masch i2, w46. c. SAUZEDDE HYDROSTATIC BRAKE SYSTEM Filed Dec. 1o, 1942 2 Sheets-Sheet .2

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` A (Ittornegsl iatented Mar. 12, 1946` nYDRos'rA'rro BRAKE SYSTEM Claude Sauzvedde, Detroit, Mich., assigner to Detroit Hydrostatic Brake Corporation, Detroit, Mich., a corporation of Michigan Application December 10, 1942, Serial No. 468,498

3 Claims. (Cl. .G0-514.5)

The present invention relates to hydrostatic'- sociated therewith for creating a sealing pres#V sure in the system during non-use of the hydrostatic brakes to prevent escape of brake fluid and to facilitate the use of self expanding sealing elements throughout the system whereby the sealing elements will be maintained in tight seall ing engagement by the sealing pressure during non-use and will be held in tight sealing contact when the brakes are applied by the developed pressure in the system.

Another object of the invention is to provide a multi-stage compressor for hydro-static brake systems having differential pistons which are sealed against the'escape of brake fluid by self expanding sealing elements formed of rubber or compositions thereof such as neoprene.

Another object of the invention is to provide a compressor unit for hydrostatic brake systems having associated therewith means for creating a sealing pressure in the compressor unit as well as in the whole system to likewise provide a sealing pressure at other locations in the system such as the brake expanding pistons and parts incident thereto.

Another object of the invention resides in providing a hydrostatic brake system with manual means for creating a sealing pressure in the system after the system has been lled or replenished with brake fluid to insure complete iilling of the system and the exclusion of air therefrom.

Another object of the invention is to provide a hydrostatic brake system including a compressor unit having differential pressure pistons for transmitting uid under pressure to the brake cylinders in. which the pressure and brake pistons are sealed against leakage of brake fluid by self expanding sealing elements, whereby a more emcient system will be provided having an increased life and requiring a minimum amount of repair work throughout its life and operation.

Other objects and advantages of the invention will become apparent during the course of the following description of the accompanying drawings, wherein:

Figure l is a longitudinal sectional view of a multi-stage compressor for fluid brake systems illustrating in detail one embodiment of the invention as applied thereto.

Figure 2 is a horizontal cross sectional view taken on line 2--2 of Fig. 1 looking in the direction of the arrows showing the manual control for creating sealing pressure in the compressor and system. n

Figure 3 is a horizontal cross sectional view taken on line 3-3 of Fig. l looking in the direction of the arrows 'illustrating the manner in which the pressure cam receiving recesses are arranged on the movabletension collar.

Figure 4 is a top plan view oi the tension collar further showing in detail the position of the cam receiving recesses. Y

Figure 5 is a side elevational View of the tension collar showing the lugs on diametrically opposed sidesA for preventing'. rotation thereof.

Figure 6 is a top plan view of the manual control member for producing sealing pressure within the multi-stage compressor and brake system.

Figure 7 is a side elevational view of the manual 'control member shown in Figure 6.

Figure 8 is a longitudinal cross-sectional view of a modified form of the invention illustrating the invention as applied to one of the pistons of the multi-stage compressor.

Figure 9 is a fragmentary cross sectional view through a portion of the compressor illustrating the pressure creating device in detail.

Figure lOis a vertical cross-sectional View taken on line l--IU of Fig. 9 looking in the direction of the arrows illustrating in detail the position and arrangement of the sealing pressure creating device. v

Figure l1 is a plan view of the manual control device for creating pressure in the brake system and multi-stager compressor.

Figure l2 is an end elevational View of one of the compressor pistons illustrating the manner in which the same is annularly cut away and provided with cam facets so as to cooperate with the manual control device, and

FigurelS is a fragmentary longitudinal cross sectional View of another modication of the invention and showing in detail the manner in which the same is associated with the compressor housing.

General description of the invention In general, the invention comprises a hydrostatic brake system employing a multi-stage or similar compressor in communication'with the working pistons of the brakes of a motor vehicle wherein one or more of the pistons ofthe compresser and working pistons may be provided with self expanding sealing elements `to prevent the escape of fluid from one side of the pistons to the other during the operating stroke of the compressor. Further, the invention consists in providing means for creating a sealing pressure in the compressor and working cylinders of the hydrostatic brake system to expand the sealing elements into tight sealing contact with their cooperating parts during non-use of the vehicle brakes thereby preventing leakage of the brake fluid between operating intervals and eliminating the loss of iluid from the system. In the preferred embodiment of the invention, the means for creating a sealing pressure is associated with one of the compensating pistons carried by the compressor and includes a manually operable decuring the flanges 22 and 24 together to exclude moisture and foreign matter from the interior of the casing 25. The free end of the casing25 terminates in a cylindrical boss 21 having an opening 28 for the passage of a plunger rod 29. The plunger 29 is provided with an aperture 30 to which the brake pedal control link may be connected in the usual manner. The inner end 3I of the plunger rod 29 is internally screw-threaded as at 32 for receiving an elongate threaded stud 33 threadedly connected as at 34 t0 the outer end of the plunger 2| to facilitate the easy assembling vice for moving the piston a predetermined distance to increase the pressure in the system within the limits of the brake shoe restraining springs.

In another form of the invention the sealing pressure producing means is coupled with one of the operating pistons of the compressor unit so that the compressor piston may be advanced a predetermined distance to create a sealing pressure within the system slightly less than the force of the brake shoe retaining springs.

Another form of the invention provides an independent cylinder and piston in communication with the compressor unit and brake system which may be manually operated to produce a sealing pressure in the system sufficient to maintain the sealing elements in close contact with their cooperating elements but insuiiicient to overcome the pressure of the brake shoe restraining springs. In all of the forms of the invention it is to be noted that the brake system may be filled when the sealing pressure devices are retracted so that the system receives an adequate amount of brake iluid before the sealing pressure is created. During the intervals between brake applications, the sealing pressure will maintain the sealing elements in their expanded position while the pressure developed during brake application likewise will act upon the sealing elements to cause expansion thereof in proportion to the pressure developed.

Detailed description of the invention In the drawings wherein for the purpose of illustrating the invention and wherein like reference characters will be employed to designate like parts throughout the same, attention isdirected to Figs. 1 to 7 inclusive wherein the reference character I will generally be employed to designate the master cylinder of a hydrostatic brake system. The master cylinder includes differential cylinder portions II and I2 in which is reciprocably mounted diierential pistons I3 and I4 respectively. The differential piston I3 nis provided with a peripheral chamber portion I5 for receiving an expansible flexible sealing element I6 formed of rubber or a similar composition such as neoprene.

Likewise the piston I3 is provided with an annular cutaway portion I1 for receiving a flexible and expansible sealing elementA I8. The expansible sealing element I8 and sealing element I6 are annular in formation and are mounted on the plunger side of the piston I3 so as to expand under pressure to create a sealing contact at the points of sealing. The piston I3 is provided with a central bore I9 surrounded by an annular sleeve forming a guide on a tubular plunger rod 2I.

The cylinder I l is provided with a ange 22 adjacent its open end and is chambered as at 23 for receiving a similar flanged portion 24 on a casing section 25. Bolts 26 are provided for seof the plunger 2I and piston rod 29. Suitably mounted on a reduced portion 35 of the plunger 2I is a collar 36 having an annular flange 31 against which abuts at one end a coil spring 36 the opposite end of which is mounted in abutting relationship with an annular ilange 39 formed integral with the plunger rod 29. The coil spring 38 is compressed between the flanges 31 and 39 and urges the collar 36 against the shoulder 4II formed by the reduced portion 35 of the plunger v rod 2 I.

The opposite end of the plunger rod 2| is provided With a longitudinal bore 4I communicating with radial ports 42 and the compression chamber 43 on the pressure side of the piston I3. The plunger 2I has its opposite end provided with a similar longitudinal bore 44 which is separated and divided from the bore 4I by means of a division wall 45. The inner end of the plunger rod 2| is beveled as at 46 and is adapted to engage a similarly beveled portion 41 on the piston I4.

Formed integral with one end of the piston I4 is an annular internal boss 48 having a passageway 49 communicating with the hollow interior 50 of said piston to allow uid passage therethrough during the initial operation of the plunger rod 29. IThe forward end of the piston I4 is formed with enlarged internal bosses 5I thereby providing a reduced bore 52 having inwardly directed spidenarms 53 for supporting a slide bearing 54. A piston packing groove 55 is formed in the marginal portion of the piston I4 for receiving a self-expanding flexible packing member 56 formed of rubber or neoprene Slidably mounted on the slide bearing 54 is a slide rod 5"! having an annular disk valve 58 adapted to close the port 52 of the piston 54 after the piston has been moved a predetermined distance. The disk valve 58 is provided with a rubber sealing 'element 59 adapted to contact the front wall of the piston and seal the port 52 against fluid passage. A nut 60 is mounted on one end of the rod 51 to retain the rod against displacement and the opposite end is provided with a head 6I forming a stop for the rod 51 against a slide bearing 62 mounted and supported in the outer end of the cylinder I2. The slide bearing 62 is formed integral with inwardly directed annular arms 63 formed on a ring 64 so that the rod 51 will be supported at each end in a slidable fashion.

Encircling the rod 57 is a coil spring 65 having one of its ends mounted in abutting relationship with the spider arm 63 and the opposite end abutting the disk valve 58 to urge said valve into engagement with the valve seat of the piston I4 after a predetermined travel of said piston has taken place.

The master cylinder casing I is provided with an annular flange 61 to accommodate a distributor head 68 likewise having formed integral there- `with an annular flange 69 adapted to be bolted by means of'bolts 70 to the flange 61. Formed integral with the distributor head B8 and extending radially therefrom are connecting members 1I for receiving the tubular fluid conduits 'l2 for conducting fluid under pressure to the brake mechanisms of the vehicle which will be described later. It is to be noted that the distributing head 68 is cut away as at I3 to provide a chamber for receiving the slide bearing supporting ring 64 and similarly, the end Wall of the master cylinder casing I9 is chambered as at 14 for receiving the opposite side of said ring S4. Packing elements may be received in the chamber portions 13 and l to seal the joints against fluid passage.

A threaded boss l is formed integral with the master cylinder casing I0 and is provided with an internally threaded bore 'lli for receiving a closure plug l1 to facilitate filling of the system with a uid such as glycerin and a combination of glycerin and oil. The internally screw-thread- L ed bore 'E9 communicates with a chamber 'i8 likewise in communication with the chamber E3 of the dilerential cylinder I l.

Formed integral with the master cylinder casing I0 is a compensating cylinder i9 having circumferentially spaced bosses 80 provided with internal threaded bores 8l. Mounted on and secured to the enlarged bosses 80 is a casing section B2 having a ange 83 adapted to be bolted in place by means of bolts 84. The casing section 82 is tapered inwardly to provide a reduced section 85 and said casing section 82 is provided with a tapered bore 86 communicating with an axial bore 8l formed in the reduced portion 85.

Bolted to the casing section 82 is a tubular portion 88 having a bore 89 alined with the axis of the cylinder T9 and said tubular portion 88 is provided with a ilange 99 adapted to be bolted to the reduced portion 85 of the casing section 82 by means of bolts 9|.

Mounted in the bore 89 of the tubular member 88 is a downwardly depending sleeve 92 having a central bore 93 and said sleeve 92 is adapted to slidably support a piston 94 on the lower end thereof as clearly shown in Fig. l.

The piston 94 is reciprocably mounted in the compensating cylinder i9 and is provided with a telescopic sleeve 95 sldably guided on the lower end of the sleeve 92 so that the piston 95| may move up and down thereon to compensate for the expansion and contraction of the brake fluid in the brake system. The bottom wall 96 of the cylinder 'I9 is provided With a boss 97 having a port or passageway 98 communicating withthe differential cylinder i2 in front of the piston M A spring 99 has one end encircling the boss 9'. at its opposite end received in an annular recess |90 of the piston 94 to urge the piston upwardly within the cylinder '|9.

Formed in the lower portion of the tubular member 88 is an annular recess IGI for rotatably receiving a collar |02 having a disk-like portion |03 provided with diametrically opposed downwardly depending cam portions |04. The disk-like portion |03 is provided with a radially extending handle portion |95 which projects through a slot |06 formed in the reduced portion 85 of the tapered casing section |32. The cutaway portion or slot |98 is of a predetermined length as indicated in Fig. 2 to allow rotation of the collar |92 a slight distance in either direction.

Slidably mounted in the bore 8l and encircling the sleeve 92 is a similar collarA |01 shown in Figs. 4 and 5 and said collar |91 is provided with diametrically opposed lugs l03'for being slidably received in diametrically opposed grooves |09 formed in the tapered casing section 82 and extending longitudinally within the reduced portion 85 thereof. The collar |07 is formed with sector shaped projections |09a which are interrupted by diametrically opposed spaces or recesses H0 and it is to be noted that the projecting cams |04 on the collar |03 are positioned so as to be received within said recesses Illl to allow the disk-like portion |93 or collar |82 and the sector shaped projection |09 to contact when the handle |95 is moved a predetermined distance.

The underside of the collar I 01 is annularly recessed as at Ill for receiving one end of a coil spring ||2, as shown clearly in Fig. l. The coil spring l l2 encircles the interlocking guide sleeve 95 of the pist-on 94 and at its opposite end is mounted in abutting relationship with a circular boss ||3 formed on the top wall of the piston 94. The piston 94 is provided with a packing groove |I4 for receiving a self-expanding sealing ring II5 similar to the pistons I3 and I4 so that the expansion of the piston rings ll5 will cause the outer periphery thereof to tightly and closely engage the inner wall of the cylinder 79.

The upper end of the guide sleeve 92 is internally threaded as at IIB and is adapted to receive a threaded nipple Ill formed on a bleed valve IIB for the purpose of removing air from the system. The bleed valve II8 is provided with a lateral projection I|9 having an internally threaded bore |29 for receiving a threaded plug |2| the outer end of which is formed polygonal as at |22 for receiving a wrench or the like while the opposite end is pointed to provide a needle valve |23 adapted to seat in a valve seat I 24 formed in the valve. A bleed duct |25 is formed in the bleed valve ||8 and communicates the interior -of the cylinder 'I9 with theatmosphere through the axial and radial ports |30 and I3| respectively in the needle valve I2 I.

The distributor head 98 is adapted to supply iiuid under pressure to the plunger cylinders of the brake construction and as shown in Fig. l, the usual brake drum |32 is provided with oppositely disposed expanding brake shoes |33. Pistons |34 are carried by the brake shoes |33 and are adapted to be mounted in opposite cylinders |35 formed integral with a casing |39. The casing is provided with ports |31 communicating with the cylinders |35 and a connection nipple |38 is threaded in the casing |36 for supplying fluid under pressure to the ducts i3? and opposed cylinders |35. Coil springs |39 are connected to the opposite brake shoes |33 to normally hold the same retracted when the brakes are not applied. A bleed valve |139 is mounted in the casing |36 as usual to allow the removal of air from the system when replenishing the brake fluid to insure maximum eiiiciency and the effective operation of the brakes.

It is to be noted that the coil spring 99 is smaller than the coil spring |l2 so that when pressure is exerted upon the spring |I2 by the rotation of the collar |02 and the removal of the cam portions |04 from the recesses Il0 the pressure of the spring 99 will be overcome sufciently to move the piston 94 downwardly a proportionate distance.

In Figs. 8 to l2 inclusive there is shown a modied form of the invention and the reference characters I4! are generally being employed to designate the master cylinder casing having a bore |42 for receiving one of the diierential pistons |43. The master cylinder casing |4I is enlarged as at |44 to provide a differential cylinder |45 for slidably receiving a piston |46 similar to the piston 3 as shown in Fig. 1. The piston 46 is provided with a central bore |41 surrounded by an annular sleeve |48 which is slidably mounted on the plunger rod |49 in the usual manner. An annular flange |50 is formed on the differential cylinder |44 for receiving the flange |52 in a cylindrical housing |53 the free end of which is formed into an annular boss |54 having a bore |55 for the projection of the plunger rod extension |51. The plunger rod |49 is formed identical to the plunger rod 2| shown in Fig. 13 hollow for a portion of its length at the end as at |58 and has its end internally threaded as at |59 for receiving an enlarged threaded member |60 having an elongated threaded portion |6| threadedly received in a horizontal opening in the plunger rod extension |51. The plunger |49 is formed with a reduced portion |62 upon which is slidably mounted a collar |63 having a flange |64 against which abuts one end of the coil spring |95 so that the opposite end may abut an annular flange |66 formed integral with the plunger rod extension |51. The coil spring |65 is compressed between the flange |64 and the annular flange |66 by assembling the spring on one end of the plunger rod extension |51 and then tightly connecting the portion |6| with the longitudinal threaded bore therein.

The piston |46 is formed with inner and outer sealing ring receiving grooves |61 and |68 respectively in which is mounted self expanding sealing rings |69 and |10 in concentric relation so that the sealing ring |69 will be expanded into engagement with the plunger rod |49 While the sealing ring |19 will be similarly expanded into engagement with the internal wall |45 of the cylinder |44. It is to be noted that the casing housing |53 is provided at one end adjacent the flange |52 with an internal cutaway portion |1| and is enlarged as at |12 at circumferentially spaced locations providing sockets |13 for receiving coil springs |14. The coil springs |14 are adapted to engage the ring member |15 having circumferentially spaced recesses |16 formed on one face thereof and as shown in Fig. 8 the rotary ring |15 is received in a groove |11 formed in the rear wall of the piston |46. A handle |18 is formed integral with the rotary ring |15 and said handle projects through a cutaway portion |19 formed in the annular flange |52 as shown in Fig. thereby providing a sector-shaped slot of predetermined length to facilitate the rotation of the ring in both directions.

The bottom wall of the annular recess |11 is provided with circumferentially spaced cam projections |80 adapted to aline with the recesses |16 when the rotary ring |15 is at the limit 0f one of its two rotational directions. Normally, with the piston |46 in its retracted position the rotary ring |15 Will be received in the annular groove |11 as shown in Fig. 8. However, when the piston |45 is moved forwardly the rotary ring will be moved out of the groove |11 during brake applications. On the other hand, when the piston |46 is in its retracted position the cam projections |80 will engage the face of the rotary ring |15 and prevent the piston |46 from moving rearwardly to a position of the plunger release.

The master cylinder casing 4| is provided with an enlarged boss |8| having a threaded filler opening |82 adapted to be closed by a filler plug |83. The ller opening |82 communicates with a chamber |84 in direct communication with the differential cylinder |44. The plungers |50 and |52 of the differential cylinder |44 and housing |53 respectively are secured together in the usual manner by bolts or the like as at |85.

In the modified form of the invention shown in Fig. 13, the master cylinder housing |86 is likewise similar to the master cylinder housings |0 and |4| in Figs. 1 to 12 inclusive and includes differential cylinders |81 and |88 formed integral in axial alinement. The cylinder 81 is provided with a hollow reciprocable piston |89 having an annular enlargement |90 presenting a beveled seat |9| adapted to be engaged by the beveled end |92 and the plunger rod |93. The plunger rod |93 is centrally hollowed and divided by a division wall |94 to form chambers |95 and |96 on opposite sides thereof. The cylindex` |88 has communication with the hollow piston |89 through the chamber |96 by Way of the ports |91 formed in the plunger |93. Slidably mounted on the plunger rod |93 is a piston |99 having a guide sleeve 200 slidable on the plunger whereby said piston may be free until the plunger |93 has moved a predetermined distance. The pressure wall of the piston is provided with concentric packing grooves 20| and 202 for receiving self expansible packing rings 203 and 204 respectively. The packing ring 203 is adapted to be expanded into sealing engagement with the plunger |93 while the packing ring 204 is expanded into sealing engagement with the bore of the cylinder |88.

Mounted on one end oi' the differential master cylinder |86 is a plunger rod housing 285 having an inclined wall 206 terminating in an annular ange 201 adapted to be bolted to a flange 208 on the master cylinder casing |86 by means of bolts 209. The free end of the plunger rod housing '205 terminates in a reduced annular portion 2|0 having a bore 2|| for allowing the free sliding movement of the plunger rod extension 2|2.

The outer end of the plunger rod extension 2|2 is provided with an aperture 2|3 for connection with the usual brake pedal linkage. The opposite end of the plunger rod extension is connected to the plunger |93 by means of a threaded member 2|4 received in an internally screwthreaded portion of the bore |95. Similarly, the inner end of the plunger rod is internally bored and threaded for receiving relatively long threaded projections formed on the threaded member 2| 4.

slidably mounted on a reduced portion 2|5 of the plunger rod |93 is a thimble 2|6 having a ange 2|1 at one end for receiving one end of a coil spring 2|8 encircling the plunger rod |93 so that the opposite end of the spring will abut an annular ilange 2|9 formed integral with the plunger rod extension 2|2.

The thimble 2|6 is limited against longitudinal movement in one direction by engaging the shoulder 220 on the plunger rod |93 and the flange 2| 1 is spaced from the sleeve 200 a slight distance so that the plunger rod |93 may move a corresponding distance during the initial portion of its stroke before engaging and moving the piston |99.

A filling chamber 22| is formed in the master cylinder casing |86 and provides a reservoir in communication with the cylinder |88. The reservoir 22| may be filled through a ller opening 222 which is suitably threaded for receiving a closure plug 223. v

Formed integral with the master cylinder cas portion 221 for receiving a spherical connection.

228 formed on the lower end of a screw-threaded rod 229. The sealing pressure cylinder 224 is open at its upper end and is internally screwthreaded for receiving an end closure member 230 having a threaded portion 23| for being threaded in the upper end of the sealing cylinder. Formed on the closure member 230 and centrally thereof is an internally screw-threaded boss 232 in which the threaded rod 229 is adjustably mounted to facilitate the adjustment of the piston 225 when the handle 233 on the upper end of the screwthreaded rod is rotated. The piston 225 is provided. with an annular packing groove 235 for receiving a self-expanding packing ring 238 similar to the packing rings 203 and 205. It is obvious that other movable elements of the brake system may be provided with self-expanding piston packings, such as the brake expanding pistons for moving the brake shoes into engagement with the brake drum.

Operation of the form of the invention shown in Figures 1 to 7 For a consideration of the operation of the invention, it will rst be assumed that the brake shoes |33 are retracted by the retention springs |39 and it is desired to apply the brakes of the vehicle to bring the same to a stop. As usual, the vehicle brake pedal is depressed causing the plunger rod extension 29 to move to the right whereupon the operating piston I i will be moved a corresponding distance while the differential piston I3 will remain at rest in its position as shown in Figure 1. During the initial movement of the plunger rod extension 28 and plunger rod 2 I, the valve 58 will remain open thereby allowing the initial movement to take place against a relatively small amount of pressure.

Upon continued movement of the plunger rod 2|, the valve 58 will have engaged the seat of the bore 52 in the piston Hi to thereby close the passage of fluid therethrough. At the instant the valve 58 is seated, the iiange 31 cn the sleeve 35 engages the piston sleeve 20 causing the plunger rod and piston 23 to move unitarily. As the pistons I3 and II! move forward in their respective cylinders, a large volume of uid in the cylinder I I is forced through the passageways 42, through the longitudinal bore il and hollow piston I4. As this movement occurs, the iiuidthus under pressure will overcome the tension of the coil spring 85 and allow the uid to pass through the part 52 and past the Valve 58.

When the pressure has thus been built up in the cylinder I2 on the pressure side of the piston I4, continued movement of the plunger rod 2| causes the valve 58 to be closed whereupon the piston I3 will slide relative to the plunger rod 2I due to the differential pressures in the cylinders II and I2. The plunger rod may be moved still further to cause the piston I4 to develop a high pressure in the brake system and during this further movement to eiiectively set the brakes |33, the coil spring will be compressed against its initial compression by reason of the ange 31 engaging the sleeve 20 and the trapped fluid under pressure in the opposite side of the piston I3.

During the above mentioned braking operation, the port 98 will be covered after the initial movement of the piston I4 to thereby cut off communication between the pressure cylinder I2 and compensating cylinder 19. However, when the brakes are retracted, the port 98 will connect the respective cylinders I2 and 19 so that expansion and contraction of the brake fluid in the system due to variation in temperature changes will be compensated for. n

When the brakes are thus applied, the selfexpanding packing rings I6, I8 and 58 will be expanded into tight sealing engagement with their cooperative surfaces to insure against theV loss of fluid under pressure. However, when the brakes are at rest, and the parts of the multistage compressor are in the position as shown in Fig. 1, a sealing pressure will be applied to the various self-expanding packing elements to retain the same in a partially expanded position sufficient to prevent the escape of fluid from the system. This may be accomplished by rotating the collar |03 a suiiicient distance by the handle |05 to cause the cam projections |04 to move out of the recesses IIO and thereby move the complemental collar |01 downwardly against the coil spring |I2. This added tension placed on the piston 94 will cause the piston to move downwardly against the action of the coil spring 99 a suicient distance to create a sealing pressure in the system incapable of overcoming the'tension of the coil springs |39, of the brake shoes |33. It has been found in practice that a pressure of 25 pounds would be sufficient to expand the packing rings |6, I 8 and 56 during non-use of the brakes to prevent escape and leakage between the respective pistons and their cylinders.

1t is intended to move the handle |05 to position the depending cams |04 in registry with the recesses |I0 of the collar |01 to allow retraction of the piston 94 when the system is being filled with brake uid to insure the proper lling of the master cylinder and other parts of the system. After the brake cylinders and master cylinders have been filled, the handle I 05 is turned to cause the cam projection I 04 to move out of the recesses IIu and thereby induce the sealing pressure in the system. Once the sealing pressure has been established. the brake system will not require any attention other than the usual check-up as is the present practice to maintain adequate brake iiuid in the system.

Operation of the form of the invention in Figures 8 to 12 inclusive The operation of the multi-stage compressor |4I is basically the same as the form shown in Figs. 1 to 7 inclusive. That is, the pistons |43 and I 46 are operated in the same manner when brake applications are made and the pressure developed in the system acts upon the brake shoes expanding pistons. The invention in Figures 8 to 12 inclusive includes the development of the sealing pressure Within the system by manipulating the cam ringr |15 in such a manner as to advance the piston |46 a suiiicient distance to create a sealing pressure in the system whereby the expansible sealing rings |69 and |10 will be urged into sealing contact with their cooperating parts. It is to be noted that the cam ring |15 is engaged by the coil springs |14 'at equidistantly circumferentially spaced points so that the springs will exert their pressure on the piston |46 when turned so as to move the recesses |16 out of alinement with the cam projections |80. Slight axial movement of the operating ring is allowed to facilitate the action of the coil springs |14 thereon. After the system has been filled with brake fluid as described, in connection with Figs. 1 to 7 inclusive, the operating ring |15 is rotated to the position shown in Fig. 9 from a position in which the recesses |15 and cam projections are in alinement to advance the piston |46. After the operating ring is thus moved, the coil springs |14 exert a pressure on the piston |46 to create a sealing pressure in the system to facilitate the expansion of the sealing rings |69 and |10 when the system is at rest. The sealing pressure is maintained at all times and is only released during the lling operation to insure complete filling of the system.

Operation of the form of the invention in Figure 13 Likewise, the operation of the multi-stage I compressor I 8B is identical to the operation of the forms of the invention shown in Figures 1 to 7 and 8 to 12 inclusive. The invention in Figure 13 is depicted in the form of a manually controlled and adjustable piston 226 reciprocably mounted in a cylinder 224 having communication with the differential cylinders of the multi-stage compressor through a duct 225. It will thus be seen tha-t by manipulating the handle 233 the piston 226 may be advancedor retracted to create a sealing pressure in the system or to relieve the pressure during filling. When the piston 228 is advanced, a sealing pressure is created in the cylinder of the multi-stage compressor as well as in the entire brake system to cause the sealing rings 203 and 204 to be expanded into tight engaging relationship with the packing grooves and 202 and the operating plunger |93 and wall of the cylinder |88. As in the other forms of the invention, the sealing pressure developed by the piston 226 is maintained constantly and is insufficient to overcome the brake show retention springs thereby preventing brake scufiing or dragging.

In the forms of the invention herewith shown and described, it is to be understood that various changes in the shape, size and arrangement of parts may be resorted to without departing from the spirit of the invention or the scope ot the' subjoined claims.

What I claim is:

1. In combination with a uid brake system having brake expanding pistons and a compressor therefor, an independent cylinder formed integral with said compressor and in communication therewith, a piston in said cylinder, a cam ring for advancing said piston, manual means for operating said cam ring and exible expansible seal ing rings for said compressor responsive to the pressure created by the independent piston whereby said sealing rings will be expanded between periods of brake application.

2. In combination with a. nuid brake system having brake expanding pistons and a compressor therefor also including a piston, a cylinder formed integral with the compressor having a port to establish communication therewith adapted to be closed after a predetermined travel of said compressor piston, a compensating piston mounted in said cylinder, a cam member located at one end oi' the cylinder, a spring interposed between the cam member and compensating piston, manual means for operating the cam member for compressing said spring and advancing said compensating piston and exible expansible sealing elements for said compressor piston and compensating piston responsive to the pressure developed by the compensating piston to maintain the sealing elements expanded between periods of brake application.

3. In combination with a fluid brake system having brake expanding pistons and a compressor therefor, an independent cylinder formed integral with the compressor and having communication therewith, a piston in said cylinder, a cam ring having cam projections mounted for partial rotation at one end of the cylinder, a collar mounted above the piston having recesses for securing said cam projections, a coil spring interposed between the piston and collar, manual means for partially rotating the cam ring to move said cam projections out of said recesses to compress the coil spring and advance the pistons and flexible expansible sealing elements for the compressor and piston responsive to the pressure created by the advancing of the piston to maintain said sealing elements expanded between periods of brake application.

CLAUDE SAUZEDDE. 

